WO2013180033A1 - 内接ギアポンプ - Google Patents

内接ギアポンプ Download PDF

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Publication number
WO2013180033A1
WO2013180033A1 PCT/JP2013/064484 JP2013064484W WO2013180033A1 WO 2013180033 A1 WO2013180033 A1 WO 2013180033A1 JP 2013064484 W JP2013064484 W JP 2013064484W WO 2013180033 A1 WO2013180033 A1 WO 2013180033A1
Authority
WO
WIPO (PCT)
Prior art keywords
suction
outer rotor
internal gear
pump chamber
discharge
Prior art date
Application number
PCT/JP2013/064484
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
宏仁 寺島
文彦 豊田
Original Assignee
アイシン精機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アイシン精機株式会社 filed Critical アイシン精機株式会社
Priority to EP13796729.5A priority Critical patent/EP2857685B1/en
Priority to BR112014029321-0A priority patent/BR112014029321B1/pt
Priority to US14/391,556 priority patent/US9765774B2/en
Priority to CN201380027045.1A priority patent/CN104364527B/zh
Publication of WO2013180033A1 publication Critical patent/WO2013180033A1/ja
Priority to IN9814DEN2014 priority patent/IN2014DN09814A/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the present invention relates to an internal gear pump.
  • a housing having a pump chamber, an outer-tooth inner rotor disposed in the pump chamber, an inner rotor disposed in the pump chamber and an inner-rotor outer rotor having a different rotational axis, and a fluid connected to the pump chamber to supply fluid
  • a suction port that communicates with the suction port
  • a discharge port that communicates with the pump chamber and discharges fluid
  • a discharge passage that communicates with the discharge port, and discharges in a direction that counteracts the force applied to the outer rotor.
  • an internal gear pump in which a groove for generating pressure is provided on an inner wall on the discharge port side (see, for example, Patent Document 1).
  • a housing having a pump chamber, an outer inner rotor disposed in the pump chamber, an inner rotor having a rotational axis different from the inner rotor disposed in the pump chamber, and a fluid connected to the pump chamber to supply fluid
  • an internal gear pump provided with an inner wall along the suction port of the pump chamber (for example, see Patent Document 2).
  • an object of the present invention is to increase the film thickness of the oil film and stabilize the behavior of the outer rotor without causing a decrease in the discharge performance of the pump.
  • the problem-solving means of the present invention includes a housing having a pump chamber, an inner rotor having an external tooth that is disposed in the pump chamber and rotates about a first rotation axis, and is disposed in the pump chamber.
  • An outer rotor having internal teeth that rotate about a rotation axis, a suction port formed in the housing, into which fluid is sucked into the pump chamber, a discharge port through which the fluid is discharged from the pump chamber, and communication with the suction port
  • An internal gear pump having a suction path and a discharge path communicating with the discharge port, wherein the pump chamber has an inner wall extending in a rotation direction of the outer rotor, and the inner wall is the first rotation
  • a first suction area extending in a circumferential direction toward the suction path from a pressing point where the outer rotor is pressed during operation, and the first suction area and the discharge area
  • a second suction area located between the outer rotor and the inner wall, and the second suction area is provided with the groove.
  • the resultant force of the interdental pressure generated between the outer teeth of the inner rotor and the inner teeth of the outer rotor, the pressure from the discharge port, and the driving force of the inner rotor is applied to the outer rotor on the inner wall. Press.
  • the groove portion that enlarges the gap increases the film thickness of the oil film, and reduces the repulsive force caused by the oil film generated between the outer rotor and the inner wall.
  • the oil film thickness increases, the oil film is crushed to absorb the repulsive force and weaken the repulsive force (the repulsive force becomes weak because the interference width by the oil film is large), and when the oil film thickness decreases, the oil film is difficult to crush Does not absorb the repulsive force and increases the repulsive force. That is, the oil film thickness and the repulsive force are inversely proportional.
  • the gap between the outer rotor and the inner wall decreases in the direction in which the outer rotor is pressed, and the position of the outer rotor and the housing is adjusted, so that the behavior of the outer rotor is stabilized and the phenomenon such as the oil whirl of the outer rotor is suppressed. Can do.
  • the groove portion is not provided in the second suction area, it is possible to secure an area where the outer rotor and the inner wall face each other through the oil film, and fluid to be discharged from the discharge path leaks into the groove, resulting in a decrease in pump discharge performance. Can be suppressed, and the behavior of the outer rotor can be further stabilized.
  • the outer rotor more than the inner wall of the groove extending from the wall of the groove in the rotational direction of the outer rotor in the second rotational axis direction sectional view of the portion where the groove is provided.
  • a configuration including a step portion extending to the side is preferable.
  • the outer rotor and the step portion come into contact with each other via the oil film, so that the repulsive force due to the oil film is adjusted by adjusting the range of the step portion,
  • the behavior of the outer rotor can be further stabilized by adjusting the position with the housing.
  • the groove portion may be configured to directly communicate with the suction passage.
  • the groove part can be discharged to the suction path side even if foreign matter has entered the groove part by directly communicating with the suction path.
  • the groove portion may be configured to communicate with the suction passage through the suction port.
  • the groove portion does not directly communicate with the suction passage, oil can be held in the groove portion, and lubrication can be performed by using the oil in the groove portion when the oil film is easily cut when the engine is started, so that the outer rotor outer circumference can be suppressed.
  • FIG. 4 is a cross-sectional view of the internal gear pump according to the first modification of the present invention taken along the line IV-IV in FIG. 3. It is a front view of the internal gear pump which concerns on the 2nd modification of this invention. It is VI-VI sectional drawing in FIG. 5 of the internal gear pump which concerns on the 2nd modification of this invention. It is a front view of the internal gear pump which concerns on the 3rd modification of this invention. It is VIII-VIII sectional drawing in FIG. 7 of the internal gear pump which concerns on the 3rd modification of this invention.
  • FIG. 1 is a front view of an internal gear pump 1 according to an embodiment of the present invention.
  • an internal gear pump 1 of the present invention includes a housing 3 having a pump chamber 2 and an inner rotor 5 having external teeth that are disposed in the pump chamber 2 and rotate around a first rotation axis 4.
  • an outer rotor 7 having an inner tooth that is disposed in the pump chamber 2 and rotates about the second rotation axis 6, a suction port 8 that is formed in the housing 3, and oil is sucked into the pump chamber 2 and the oil is pumped It has a discharge port 9 that is discharged from the chamber 2, a suction path 10 that communicates with the suction port 8, and two discharge paths 11 that communicate with the discharge port 9.
  • the pump chamber 2 has a perfect inner wall 12 extending in the rotation direction of the outer rotor 7, and the inner wall 12 is bounded by a plane A including the first rotation axis 4 and the second rotation axis 6. And a suction region A1 on the suction port 8 side, and a discharge region A2 on the discharge port 9 side from the boundary.
  • the outer rotor 7 is pressed.
  • a first suction region B2 extending in the circumferential direction from the pressing point B1 located at a position where the outer rotor 7 is pressed when the internal gear pump 1 is operated in the suction region A1; It has 2nd suction area
  • a groove portion 13 is provided in the axial direction of the second rotating shaft core 6 so as to communicate from the suction passage 10 to the pressing point B1, and the gap between the outer rotor 7 and the inner wall 12 is expanded.
  • the groove 13 is not formed in the region B3, and the outer rotor 7 and the inner wall 12 are in contact with each other through the oil film in the second suction region B3.
  • the groove part 13 should just be formed in the part in 1st suction area
  • FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1 of the internal gear pump 1 according to the embodiment of the present invention.
  • a step portion 15 extending from the circumferential bottom portion 14 (groove inner wall) of the inner wall 12 in the groove portion 13 to the outer rotor 7 side is provided.
  • the step portion 15 and the bottom portion 14 extend from the suction port 8 in the circumferential direction of the inner wall 12 in a stepped shape, and the outer rotor 7 and the step portion 15 come into contact with each other through the oil film.
  • Oil is supplied between the outer teeth of the inner rotor 5 and the inner teeth of the outer rotor 7 that change in volume in the increasing direction from the suction passage 10 through the suction port 8 on the suction region A1 side.
  • the oil sucked in the suction area A1 is discharged to the discharge path 11 through the discharge port 9 from between the outer teeth of the inner rotor 5 and the inner teeth of the outer rotor 7 whose volume changes in the decreasing direction on the discharge area A2 side.
  • oil enters the gaps between the members such as the housing 3, the inner rotor 5, and the outer rotor 7, and these members come into contact with each other through an oil film.
  • the inner rotor 5 is given a driving force and rotates counterclockwise in FIG. 1 around the first rotation axis 4, and the outer rotor 7 is driven by the inner rotor 5 and around the second rotation axis 6.
  • the oil is supplied between the outer teeth of the inner rotor 5 and the inner teeth of the outer rotor 7 in the suction area A1
  • the oil is supplied between the outer teeth of the inner rotor 5 and the outer rotor 7 in the discharge area A2. It discharges from between the inner teeth.
  • a vector from the second rotating shaft 6 is obtained by the resultant force of the interdental pressure generated between the outer teeth of the inner rotor 5 and the inner teeth of the outer rotor 7, the pressure from the discharge port 9, and the driving force of the inner rotor 5.
  • the outer rotor 7 is pressed in the B direction, and the outer rotor 7 is pressed against the inner wall 12 toward the pressing point B1.
  • the groove portion 13 that enlarges the gap increases the film thickness of the oil film, and reduces the repulsive force caused by the oil film generated between the outer rotor 7 and the inner wall 12.
  • the oil film thickness and the repulsive force are inversely proportional.
  • the gap between the outer rotor 7 and the inner wall 12 decreases in the direction in which the outer rotor 7 is pressed, and the position of the outer rotor 7 and the housing 2 is adjusted, so that the behavior of the outer rotor 7 is stabilized, and the oil whirl of the outer rotor 7 Such a phenomenon can be suppressed.
  • the groove portion 13 is not provided in the second suction region B3, an area where the outer rotor 7 and the inner wall 12 face each other through the oil film can be secured, and oil to be discharged from the discharge path 11 leaks into the groove 13.
  • the outer rotor 7 and the step part 15 contact
  • the groove portion 13 extends in the circumferential direction until reaching the suction passage 10 and communicates directly with the suction passage 10, so that even when foreign matter enters the groove portion 13, the groove portion 13 can be discharged to the suction passage 10 side. it can.
  • FIG. 3 is a front view of the internal gear pump 1 according to the first modification of the present invention
  • FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3 of the internal gear pump 1 according to the first modification of the present invention.
  • the difference from the embodiment shown in FIGS. 1 and 2 is that the groove portion 13A communicates directly with the suction port 8 without a step.
  • the groove portion 13A communicates directly with the suction port 8, so that the oil film force generated between the outer rotor 7 and the inner wall 12 can be further reduced. Further, even when a foreign substance has entered the groove 13A, it can be more positively discharged to the suction port 8 and the suction passage 10.
  • FIG. 5 is a front view of the internal gear pump 1 according to the second modified example of the present invention
  • FIG. 6 is a cross-sectional view taken along the line VI-VI in FIG. 5 of the internal gear pump 1 according to the second modified example of the present invention.
  • the groove 13 ⁇ / b> B does not extend until reaching the suction path 10, and communicates with the suction path 10 via the suction port 8, and directly communicates with the suction path 10. It is a point not to do.
  • the inner wall 12A that contacts the outer rotor 7 is provided between the suction passage 10 and the groove 13B.
  • the groove portion 13B does not directly communicate with the suction passage 10, so that the oil can be held in the groove portion 13B, and the oil in the groove portion 13B is used when the oil film is easily cut when the engine is started. Therefore, wear on the outer periphery of the outer rotor 7 can be suppressed.
  • FIG. 7 is a front view of the internal gear pump 1 according to the third modification of the present invention
  • FIG. 8 is a cross-sectional view taken along the line VIII-VIII in FIG. 7 of the internal gear pump 1 according to the third modification of the present invention.
  • the difference from the second modification shown in FIGS. 5 and 6 is that the groove 13C communicates directly with the suction port 8 without a step.
  • the groove 13C communicates directly with the suction port 8, so that the oil film force generated between the outer rotor 7 and the inner wall 12 can be reduced as compared with the second modification. Moreover, even when a foreign substance has entered the groove 13C, it can be more actively discharged to the suction port 8 and the suction path 10 side.
  • the internal gear pump according to the present invention can be used for vehicle hydraulic devices, general machinery hydraulic devices, and other hydraulic systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
PCT/JP2013/064484 2012-06-01 2013-05-24 内接ギアポンプ WO2013180033A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP13796729.5A EP2857685B1 (en) 2012-06-01 2013-05-24 Internal gear pump
BR112014029321-0A BR112014029321B1 (pt) 2012-06-01 2013-05-24 Bomba de engrenagem interna
US14/391,556 US9765774B2 (en) 2012-06-01 2013-05-24 Internal gear pump
CN201380027045.1A CN104364527B (zh) 2012-06-01 2013-05-24 内接齿轮泵
IN9814DEN2014 IN2014DN09814A (enrdf_load_stackoverflow) 2012-06-01 2014-11-19

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-126373 2012-06-01
JP2012126373A JP5783136B2 (ja) 2012-06-01 2012-06-01 内接ギアポンプ

Publications (1)

Publication Number Publication Date
WO2013180033A1 true WO2013180033A1 (ja) 2013-12-05

Family

ID=49673229

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/064484 WO2013180033A1 (ja) 2012-06-01 2013-05-24 内接ギアポンプ

Country Status (7)

Country Link
US (1) US9765774B2 (enrdf_load_stackoverflow)
EP (1) EP2857685B1 (enrdf_load_stackoverflow)
JP (1) JP5783136B2 (enrdf_load_stackoverflow)
CN (1) CN104364527B (enrdf_load_stackoverflow)
BR (1) BR112014029321B1 (enrdf_load_stackoverflow)
IN (1) IN2014DN09814A (enrdf_load_stackoverflow)
WO (1) WO2013180033A1 (enrdf_load_stackoverflow)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6985884B2 (ja) * 2017-10-20 2021-12-22 株式会社山田製作所 スカベンジポンプ

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63195391A (ja) * 1987-02-10 1988-08-12 Sumitomo Electric Ind Ltd トロコイド式ギヤ−ポンプ
US20090196772A1 (en) * 2008-02-05 2009-08-06 Hitachi, Ltd. Oil Pump
JP4792342B2 (ja) * 2006-07-19 2011-10-12 日立オートモティブシステムズ株式会社 内接歯車ポンプおよびパワーステアリング装置

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Publication number Priority date Publication date Assignee Title
US2434135A (en) * 1942-12-02 1948-01-06 Eaton Mfg Co Gear pump structure
US2522824A (en) * 1944-08-29 1950-09-19 Thomas L Hicks Rotary compressor
JPH08312539A (ja) * 1995-05-15 1996-11-26 Toyo A Tec Kk 内接歯車ポンプ
CN2348150Y (zh) * 1998-08-28 1999-11-10 上海浦东龙盛印染机械有限公司 内啮合齿轮浆泵
GB9922360D0 (en) * 1999-09-22 1999-11-24 Hobourn Automotive Ltd Improvements relating to pumps
JP4600612B2 (ja) * 2000-03-22 2010-12-15 株式会社ジェイテクト 内接歯車式ポンプ装置
JP2003035277A (ja) * 2001-07-24 2003-02-07 Nachi Fujikoshi Corp トロコイドポンプ
JP3801536B2 (ja) * 2002-06-27 2006-07-26 アイシン・エィ・ダブリュ株式会社 内接歯車式オイルポンプおよびこれを備えた自動変速機
CN201129295Y (zh) * 2007-08-17 2008-10-08 宁波高新协力机电液有限公司 高压内啮合齿轮泵内齿圈静压卸荷装置
JP2012057561A (ja) * 2010-09-10 2012-03-22 Sumitomo Electric Sintered Alloy Ltd 内接歯車式オイルポンプ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63195391A (ja) * 1987-02-10 1988-08-12 Sumitomo Electric Ind Ltd トロコイド式ギヤ−ポンプ
JP4792342B2 (ja) * 2006-07-19 2011-10-12 日立オートモティブシステムズ株式会社 内接歯車ポンプおよびパワーステアリング装置
US20090196772A1 (en) * 2008-02-05 2009-08-06 Hitachi, Ltd. Oil Pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2857685A4 *

Also Published As

Publication number Publication date
CN104364527B (zh) 2016-10-05
EP2857685B1 (en) 2017-01-11
EP2857685A4 (en) 2015-06-24
JP2013249806A (ja) 2013-12-12
CN104364527A (zh) 2015-02-18
EP2857685A1 (en) 2015-04-08
BR112014029321A2 (pt) 2017-06-27
BR112014029321B1 (pt) 2021-06-22
IN2014DN09814A (enrdf_load_stackoverflow) 2015-07-31
US20150064038A1 (en) 2015-03-05
US9765774B2 (en) 2017-09-19
JP5783136B2 (ja) 2015-09-24

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